US20070209611A1 - Multicylinder internal combustion engine with individual cylinder assemblies - Google Patents
Multicylinder internal combustion engine with individual cylinder assemblies Download PDFInfo
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- US20070209611A1 US20070209611A1 US11/751,138 US75113807A US2007209611A1 US 20070209611 A1 US20070209611 A1 US 20070209611A1 US 75113807 A US75113807 A US 75113807A US 2007209611 A1 US2007209611 A1 US 2007209611A1
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- cylinder
- valve lifter
- internal combustion
- carrier
- combustion engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0021—Construction
- F02F7/0031—Construction kit principle (modular engines)
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/146—Push-rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/054—Camshafts in cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/021—Cooling cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/024—Cooling cylinder heads
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
- Y10T29/49231—I.C. [internal combustion] engine making
Definitions
- the present invention relates to an internal combustion engine having individual cylinder assemblies which are mounted upon a cylinder carrier.
- the cylinder carrier may itself be modularized.
- the present inventive modular structure is ideally suited to either naturally aspirated engines or engines operated at high specific output, such as turbocharged or supercharged diesel and gasoline engines.
- an engine according to the present invention solves the problems described above by providing a true modular construction for the power cylinders.
- the cylinder carrier is itself modular. All of the present inventive engines utilize direct fresh water cooling, with individual cooling flows directed to each of the cylinder assemblies. In this manner, the present engine is ideally suited for charge air boosting to fairly high pressures, because the engine offers superior cooling capability as compared with prior art engines.
- a liquid-cooled internal combustion engine includes a plurality of cylinder assemblies mounted individually to a common cylinder carrier. Each cylinder assembly houses a single piston and has a cylinder portion with a cylinder bore, a cylinder head with at least one intake port, and at least one exhaust port, as well as at least one self-contained cooling passage.
- the present engine also includes a common-rail coolant inlet manifold for introducing an individual coolant flow to each of the self-contained cooling passages within the cylinder assemblies, and an exhaust manifold assembly mounted to each of the cylinder heads, with the exhaust manifold including a plurality of branch passages for receiving exhaust from each of the exhaust ports.
- the exhaust manifold further includes a number of separate intake coolant passages for conducting coolant flowing from each of the self-contained cooling passages in the cylinder head about an exterior portion of a mating one of each of the exhaust manifold's branch passages.
- the self-contained cooling passages in each cylinder assembly extend about the cylinder portion and cylinder head.
- the coolant is introduced by the coolant inlet manifold into each of the self-contained passages at a location proximate a lower portion of the cylinder portions, so that coolant is first permitted to flow about the cylinder portion, and then about the cylinder head, prior to being discharged into the exhaust manifold at a location proximate the exhaust port corresponding to the particular cylinder in question.
- Coolant for the cylinders and cylinder head of the present engine is circulated by means of a primary water pump which circulates either fresh water, or a glycol and water solution, through the cylinder assemblies and then through the cylinder heads into the exhaust manifold. While in the exhaust manifold, a heat exchanger mounted within the manifold transfers heat from coolant flowing from the cylinder assemblies to raw water flowing through a heat exchanger located in the exhaust manifold.
- a liquid-cooled charge air intercooler is furnished with raw water directly by a raw water pump.
- a liquid-cooled engine oil cooler is furnished with raw water directly by the raw water pump.
- Raw water is also furnished directly to the previously described heat exchanger situated within the exhaust manifold.
- a secondary fluid cooler located downstream from the intercooler transfers heat from a secondary fluid, such as hydraulic fluid, or transmission fluid, or fuel, to raw water flowing from the intercooler.
- a secondary fluid such as hydraulic fluid, or transmission fluid, or fuel
- a turbocharger mounted on an engine according to the present invention preferably includes a cooling jacket for receiving raw water flowing from the oil cooler.
- a method for cooling a multi-cylinder internal combustion engine includes the steps of cooling a number of cylinder assemblies by providing an individual flow of fresh water to each of a corresponding number of discrete cooling passages. A separate, discrete cooling passage is routed to and through each of the cylinder assemblies.
- the present method also includes the step of extracting heat from the fresh water flowing from the cylinder assemblies by means of a direct raw water cooled heat exchanger.
- the present method also includes the step of extracting heat from a charge air intercooler by providing a direct raw water flow to the intercooler.
- the present method may include the step of extracting heat from lubricating oil flowing through the engine by means of a heat exchanger cooled by direct raw water flow.
- a cylinder carrier includes a plurality of cylinder mounting modules and a plurality of main bearing bulkheads interposed between and interconnecting adjacent ones of the cylinder mounting modules.
- a crankshaft is mounted to the main bearing bulkheads.
- the mechanical strength of the cylinder carrier is enhanced by structural rails, extending longitudinally along the periphery of the cylinder carrier, parallel to the crankshaft's centerline. These structural rails extend vertically and downwardly from a position above the centerline of the crankshaft, to an oil pan.
- Each of the cylinder mounting modules preferably comprises a light alloy casting, with each of the main bearing bulkheads preferably comprising a ferrous body.
- cylinder mounting modules may be formed as aluminum castings, with the main bearing bulkheads being grey or nodular iron, cast steel or other ferrous compositions.
- the main bearing bulkheads may be fabricated from a light alloy.
- the present engine further includes a single camshaft extending parallel to the crankshaft centerline.
- the camshaft operates at least one intake valve and at least one exhaust valve for each of the individual cylinder heads.
- the camshaft operates the valves by means of at least two rocker shafts extending across an upper portion of each of the cylinder heads in a direction generally perpendicular to the crankshaft centerline.
- a method for removing and reinstalling an individual cylinder assembly of an internal combustion engine includes the steps of draining coolant from the engine and removing a plurality of fasteners extending from a cylinder carrier upwardly through a cylinder portion and through a cylinder head. Thereafter, the cylinder head and cylinder portion are lifted from the engine and a wrist pin is shifted left or right within the piston so as to allow the piston to be separated from its connecting rod. Then, a new piston and wrist pin are installed upon the connecting rod and a new cylinder portion is installed upon the piston by sliding a piston ring compression zone of the cylinder portion over a plurality of piston rings carried upon the piston.
- each of the cylinder portions has a ferrous cylinder sleeve pressed in place in the cylinder portion.
- a method for replacing crankshaft main bearing inserts in a reciprocating internal combustion engine includes the steps of removing an oil pan mounted to structural rails of the bottom of the engine's crankcase, and then removing at least one of the structural rails extending longitudinally along a portion of a cylinder carrier parallel to the crankshaft's centerline.
- the structural rail also extends vertically from a position above the centerline of the crankshaft to the oil pan.
- At least two valve lifters are provided for each cylinder.
- the lifters are slidingly housed within valve lifter sleeves mounted within bores formed in a deck surface of the engine's cylinder carrier.
- Each of the lifter sleeves includes a generally circular, hollow cylinder having a flange at one end, which engages a counterbore formed in the deck surface.
- each valve lifter has a center bore for feeding lubrication to a pushrod riding upon the lifter.
- a radially directed passage conducts lubricant to the center bore from an annular lubrication collection passage circumscribing a portion of the outer periphery of the valve lifter. Oil, which moves upwardly through the pushrods, is allowed to flow through drainback passages formed in the lifters, so that the camshaft's lobes are lubricated.
- a method for installing a cylinder poppet valve operating system in an internal combustion engine includes installing a camshaft in a cylinder carrier having a deck surface; installing a valve lifter sleeve in a bore formed through the deck surface; installing a valve lifter in the lifter sleeve; and installing a cylinder assembly upon the deck surface, such that the cylinder assembly contacts a portion of the valve lifter sleeve, whereby the valve lifter sleeve will be retained within the lifter bore.
- a pushrod is installed through a passage within the cylinder assembly, such that the pushrod is in contact with an upper surface of the valve lifter.
- a rocker arm assembly may be installed upon a cylinder head mounted at an upper portion of the cylinder assembly.
- valve lifter and lifter sleeve arrangement allows the upper portion of the engine's cylinder assemblies to be lubricated without the need for the extensive machining which accompanies the provision of multiple oil passages in conventional engines.
- FIG. 1 is a perspective view of an engine according to the present invention.
- FIG. 2 is similar to FIG. 1 , but shows the engine of FIG. 1 with the exhaust manifold assembly removed.
- FIG. 3 illustrates various flow paths for the primary, or fresh water, cooling system of an engine according to the present invention.
- FIGS. 4A and 4B show an exhaust manifold according to the present invention.
- FIGS. 5A and 5B illustrates a liquid-cooled exhaust manifold suitable for use with a non-marine engine according to the present invention.
- FIG. 6 is a cutaway perspective view of a cylinder assembly according to the present invention.
- FIG. 7 is similar to FIG. 3 but shows additional aspects of a raw water cooling system and flows according to the present invention.
- FIG. 8 illustrates the flow path through an intercooler of an engine according to the present invention.
- FIG. 9 illustrates a primary or fresh water cooling system path of a non-marine engine according to the present invention and having a radiator.
- FIG. 10 is similar to FIG. 9 but shows the secondary cooling system path of a non-marine engine according to the present invention and having a radiator.
- FIG. 11 illustrates placement of the main bearing caps in an engine according to the present invention.
- FIG. 12 illustrates placement of a crankshaft within an engine according to the present invention.
- FIG. 13 illustrates a unitary cylinder carrier according to one aspect of the present invention having a cylinder assembly 16 mounted thereto.
- FIG. 14 is an exploded view of a modular cylinder carrier according to one aspect of the present invention.
- FIG. 15 illustrates the components of FIG. 14 after assembly into an engine carrier.
- FIG. 16 is a view, partially in section, and partially an elevation, showing a valve lifter sleeve, a valve lifter, and associated hardware according to the present invention.
- FIG. 17 is a perspective view of a valve lifter sleeve according to one aspect of the present invention.
- FIG. 18 is a perspective view of a valve lifter according to one aspect of the present invention.
- FIG. 19 is a plan view of a valve lifter of FIG. 18 .
- FIG. 20 is a perspective view of a valve lifter slidingly carried within a valve lifter sleeve according to the present invention.
- FIG. 21 is an exploded perspective view of an engine showing various features according to the present invention.
- engine 10 is an inline engine which is turbocharged and which has a liquid-cooled exhaust manifold for marine use.
- a primary water pump, 128 circulates fresh water through exhaust manifold assembly 74 , as well as through the cylinder assemblies 16 , which are shown more clearly in FIGS. 2, 6 , and 13 .
- fresh water has the conventional meaning: i.e., coolant which is not extracted from a body of water upon which a vessel is being operated, but rather is cooled by a heat exchanger.
- Each cylinder assembly 16 which is shown freestanding in FIG.
- Cylinder portion 18 includes cylinder portion 18 , having a cylinder bore 20 , which is normally fitted with a honed iron sleeve.
- Cylinder portion 18 is preferably cast from a light alloy such as an aluminum or magnesium alloy. Alternatively, other metals such as iron could be employed for forming cylinder portion 18 .
- Cylinder head 22 is mounted to an upper portion of cylinder portion 18 . Cylinder head 22 , as shown in FIG. 6 , also includes intake port 26 and exhaust port 23 .
- FIG. 13 depicts a fuel injector, 182 , which may comprise either a diesel injector, a gasoline injector, a natural gas injector, a nitrous oxide injector, or yet other types of fuel injectors known to those skilled in the art and suggested by this disclosure. At least one injector 182 is mounted to each of cylinder assemblies 16 .
- FIGS. 1, 2 , 3 , and 9 illustrate coolant supply manifold 68 , which functions as a common rail to provide an individual coolant flow to self-contained cooling passages located within cylinder assembly 16 ( FIG. 13 ).
- each of cylinder assemblies 16 is provided with coolant, which has not flowed through other cylinder assemblies.
- coolant enters cylinder assembly 16 through coolant inlet port 46 and then travels through water jacket 48 located about cylinder bore 20 . After circulating about water jacket 48 , coolant flows through transfer ports 52 and up into transverse cooling passage 56 formed within cylinder head 22 . After having flowed through transverse cooling passage 56 , coolant exits cylinder head 22 by means of coolant outlet ports 62 .
- These coolant outlet ports are shown in FIG. 6 , as well as in FIG. 2 .
- Tube bundle 100 is cooled by means of a direct raw water flow provided by raw water pump 118 which is shown in FIGS. 1, 2 , 7 , and 10 .
- Raw water is furnished to one end of tube bundle 100 located at the front of the engine, as shown in FIG. 7 , and having traversed the length of tube bundle 100 and with the raw water traveling inside the numerous small tubes of the tube bundle, the raw water exits and flows into exhaust elbow 58 . Because raw water is provided directly to coolant heat exchanger 92 , high efficiency cooling is achieved, so as to allow high boosting rates with the present engine.
- raw water pump 118 has inlet 120 which picks up raw water at ambient temperature from a lake, river, or ocean. The flow is immediately split into three separate flows. A first single flow passes through engine oil cooler 124 and then to turbocharger cooling jacket 146 , which surrounds a portion of turbocharger 144 . After flowing through turbocharger cooling jacket 146 , the water flows into exhaust elbow 58 . The second single flow of the raw water flow split from raw water pump 118 flows, as previously described, through the engine's fresh water cooling system heat exchanger.
- the third separate flow of the raw water split from the flow through raw water pump 118 flows through intercooler coil 112 (not visible), located inside intake manifold 106 which is shown in FIG. 8 and receives direct raw water flow from pump 118 .
- Air arriving at intake manifold 106 passes from turbocharger 144 into air inlet 110 and then flows upwardly through intercooler heat exchanger 112 and into intake ports 26 of cylinder assemblies 16 visible on FIG. 13 .
- the raw water is at a much colder temperature than would otherwise be the case were the water to be used to cool some other part of the engine, such as the engine oil cooler, before entering intercooler 112 . This is not the case with known engines.
- Raw water leaving intercooler 112 passes through secondary fluid cooler 138 , which is shown in FIG. 8 .
- Cooler 138 may be used for the purpose of extracting heat from transmission fluid, or other types of fluids used in a vehicle or boat having the present engine.
- Coolant expansion tank 132 is mounted at the opposite end of the engine from secondary fluid cooler 138 . Expansion tank 132 accounts for the fact that known engine coolants generally have a positive coefficient of thermal expansion. Expansion tank 132 allows for this expansion without the necessity of admitting air into the cooling system.
- FIGS. 5A and 5B illustrate an exhaust manifold, 76 , suitable for use with a non-marine variant of the present engine.
- the manifold 76 of FIGS. 5A and 5B is, however, liquid-cooled and the annular discharge coolant passages 84 are readily ascertainable in FIG. 5A .
- FIGS. 5A and 5B may be combined with the radiator, 126 , illustrated in FIG. 9 .
- the primary fresh water cooling system shown in FIG. 9 is separated from the secondary cooling system shown in FIG. 10 .
- both systems rely on the rejection of heat to the ambient air, which radiators 126 and 127 provide.
- Note in FIG. 10 that a salient feature of the present invention resides in the fact that cooled water from radiator 127 , is used for the purpose of providing water to the cooling circuits furnished with raw water in the marine embodiments described earlier.
- the two cooling circuits would likely be combined into one, with the use of a single sufficiently large radiator and a single sufficiently large pump with a split pump discharge providing the coldest possible coolant flow to the engine coolant supply manifold, oil cooler, and intercooler. Cooling of the turbocharger is not normally required in a vehicular application.
- FIGS. 11-15 Details of the bottom end of the present engine are shown in FIGS. 11-15 .
- the engines shown in FIGS. 11, 12 and 13 include a unitary cylinder carrier, 30 , providing a base for a plurality of cylinder assemblies 16 ( FIG. 13 ).
- FIGS. 14 and 15 show a modular cylinder carrier for a four-cylinder engine in which four separate mounting modules 156 are joined together by means of three main bearing bulkheads 160 . Cylinder mounting modules 156 and bulkheads 160 are maintained in an assembly by means of threaded fasteners (not shown).
- FIG. 15 shows a completed cylinder carrier 30 which also includes an end bulkhead, 161 , at the front of the engine. Bulkhead 161 has provisions for the front engine mounts.
- a rear bulkhead, 162 is provided for terminating the rear end of the modular cylinder carrier 30 shown in FIGS. 14 and 15 . It is easily seen from FIGS. 14 and 15 that an engine according to the present invention may be assembled with varying numbers of cylinders merely by adding more or fewer cylinder mounting modules 156 and bulkheads 160 .
- FIGS. 11 and 12 illustrate a feature providing for ready disassembly and repair of the present engine even when the engine is mounted within a watercraft, a motor vehicle, or another piece of machinery.
- Cylinder carrier 30 whether of a one-piece configuration as shown in FIGS. 11, 12 and 13 , or in a modular configuration as shown in FIGS. 14 and 15 , extends downwardly only to a position above the centerline of the crankshaft and main bearing bores.
- inserts 176 for each of the main bearings of crankshaft 166 may readily be removed from engine 10 once the appropriate main bearing cap 168 ( FIG. 11 ) has been removed.
- FIGS. 1 & 2 Removal of main bearing inserts 176 is aided by the removability of structural rails 170 ( FIGS. 1 & 2 ).
- Structural rails 170 are used on both sides of engine 10 .
- rails 170 allow ready access to fasteners for main bearing caps 168 ( FIG. 11 ). After rails 170 have been removed from engine 10 , as explained below, by removing the fasteners from oil pan 174 , crankshaft bearings 176 are exposed, as may be visualized from FIGS. 11 and 12 .
- a method for replacing crankshaft main bearing inserts in a reciprocating internal combustion engine includes the steps of removing oil pan 174 and then removing structural rail 170 from at least one side of engine 10 .
- Structural rail 170 , oil pan 174 , and cylinder carrier 30 are attached to another by means of through bolts 172 ( FIG. 1 ) which extend through oil pan 174 , and then through passages formed in structural rails 170 , and into suitably tapped holes within carrier 30 .
- through bolts 172 FIG. 1
- main bearing caps 168 may be removed serially and the bearing inserts renewed using conventional techniques.
- the present engine permits ready removal and reinstallation of an individual cylinder assembly.
- Experience shows that frequently, only one cylinder of an engine may be worn excessively. All too often with mono-block engines, it becomes necessary to scrap the entire block because it is not possible to rebore the cylinder. Even if reboring is an option, in an engine application such as a pleasure boat, it is not possible to machine anything on the cylinder block without removing the engine from the boat. Such removal is extremely costly, and particularly so, in the case of boats having multiple decks above the engine room.
- the steps for such removal and reinstallation include draining coolant from engine 10 , removing a plurality of fasteners 172 extending from cylinder carrier 30 upwardly through cylinder portion 18 and cylinder heads 22 , and lifting cylinder head 22 and cylinder portion 18 from carrier 30 . Then, wrist pin 36 may be removed and a new piston, 32 , installed upon connecting rod 40 . Thereafter, cylinder portion 18 may be slidably installed upon piston 32 by sliding piston ring compression zone 178 ( FIG. 6 ) over piston 20 and its piston rings.
- piston ring compression zone 178 makes it possible to reinsert pistons 32 into the bottom of cylinder bores 20 without the need of any additional ring compressor or other device. Also, it should be noted that with the exception of crankshaft 166 , no machining is required to rebuild an engine according to the present invention.
- FIGS. 12 and 16 illustrate aspects of the valve actuation portion of the present engine system.
- Carrier 30 has crankshaft 166 and camshaft 186 installed therein, with camshaft 186 having a plurality of lobes, 190 , which actuate the valve train as follows.
- Valve lifters 200 are situated within valve lifter sleeves 194 , which in turn are sited within valve lifter bores 192 formed within cylinder carrier 30 .
- bore 192 has a counter bore, 196 , which, as noted below, engages a flange formed at an end portion of valve lifter sleeve 194 .
- valve lifter 200 is mounted within valve lifter sleeve 194 and contacts a lower end of a push rod, 204 .
- cam lobe 190 raises lifter 200
- push rod 204 will correspondingly be raised.
- Push rod 204 passes through the cylinder portion 18 of cylinder assembly 16 through a passageway, 208 , to an upper portion of cylinder assembly 16 .
- FIG. 17 shows various details of valve lifter sleeve 194 .
- Sleeve 194 is configured as a generally circular hollow cylinder having a cylindrical outer surface 218 and an upper flange 222 , which engages counter bore 196 formed in deck 200 of carrier 30 .
- Flange 222 prevents lifter sleeve 194 from moving downwardly within valve lifter bore 192 past the design location for lifter sleeve 194 .
- lifter sleeve 194 is mounted in a depending orientation within lifter bore 192 .
- valve lifter sleeve 194 has an annular groove, 226 , in the upper surface of upper flange 222 , which provides a mounting location for a sealing O-ring (not shown) which is engaged by cylinder portion 18 of cylinder assembly 16 when cylinder portion 18 is bolted to carrier 30 . Accordingly, cylinder assembly 16 prevents lifter sleeve 194 from becoming disengaged with carrier 30 .
- Lifter sleeve 194 has an indexing surface or flatted area, 214 , aligned with an elongated, radially directed oil passage, 228 .
- Passage 228 receives oil from a pressurized oil galley, 197 ( FIG. 16 ), within carrier 30 and allows oil to pass through to lifter 200 , as described below.
- Indexing feature 214 prevents lifter sleeve 194 from rotating to a position at which oil passage 228 is not properly indexed with oil passage 197 .
- lifter 200 has a generally cylindrical body, 230 , with a lower end, 234 , which is adapted for contact with one of lobes 190 of camshaft 186 .
- Body 230 of lifter 200 also has an upper end, 240 , having a hemispherical depression, 238 , shown with specificity in FIG. 18 .
- Hemispherical depression 238 engages one of valve operating push rods 204 as shown in FIG. 16 .
- Each of valve lifters 200 has a center bore, 242 , which feed oil up through hollow push rods 204 to the upper part of cylinder assembly 16 .
- the oil is furnished to center bore 242 by means of a radially directed passage, 246 , formed in lifter body 230 .
- Radially directed passage 246 allows communication with an annular lubrication collection passage, 250 , which circumscribes a portion of the outer cylindrical surface of lifter body 230 .
- passage 228 formed in lifter sleeve 194 is located so as to be in hydraulic communication with annular lubrication collection passage 250 formed in lifter body 230 .
- Drainback passages 254 extend axially through the greater part of valve lifter body 230 so that lubricating oil will be allowed to flow down through body 230 and then to exit into drainback annulus 258 ( FIG. 19 ), from which the oil drains down over the lowermost portion of the outer surface of lifter body 230 , and then onto camshaft 186 ( FIG. 16 ).
- FIG. 21 is an exploded perspective view showing unitary carrier 30 , with a structural rail, 170 , and oil pan 174 , according to the present invention.
- FIG. 21 also shows assembly of valve lifter sleeves 194 and valve lifters 200 into lifter bores 192 , complete with counter bores 196 within cylinder carrier 30 .
- FIG. 21 shows that valve lifters 200 are telescopically nested into valve lifter sleeves 194 .
- the use of valve lifter sleeves 194 permits an engine constructed according to the present invention to be rebuilt in the field without the use of expensive machining services and indeed, without the necessity of removing an engine from a vehicle or watercraft or other piece of equipment.
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Abstract
Description
- The present application is a continuation-in-part of U.S. application Ser. No. 11/163,947 filed Nov. 4, 2005, which claims priority to U.S. Provisional Patent Application 60/626,622 and 60/626,623, filed Nov. 10, 2004, and U.S. Provisional Patent Application 60/658,078 and 60/658,079, filed Mar. 3, 2005.
- The present invention relates to an internal combustion engine having individual cylinder assemblies which are mounted upon a cylinder carrier. The cylinder carrier may itself be modularized. The present inventive modular structure is ideally suited to either naturally aspirated engines or engines operated at high specific output, such as turbocharged or supercharged diesel and gasoline engines.
- The vast majority of multi-cylinder internal combustion engines sold today utilize a single cylinder block containing a plurality of cylinder and valve lifter bores. Unfortunately, if one of the cylinder bores or valve lifter bores becomes damaged to the point where it cannot be repaired by sleeving or by other means commonly used for such repairs, the entire cylinder block must be scrapped. Another drawback characterizing conventional engines resides in the engines' cooling systems. Most engines use a cooling circuit in which water is drawn into a lower portion of the engine, particularly the cylinder block, at only a single location, and then allowed to flow along the length of the cylinder block, while a portion of the water flowing along the length of the cylinder block, and eventually, all of the water, flows upwardly through the cylinder head of the engine. Then, water flows along cooling passages formed within the cylinder head and out of the engine, again at a single location. A drawback of this type of cooling system resides in the fact that the coolant must travel a fairly long path through the engine, and as a result, the coolant becomes quite heated and therefore unable to transfer as much heat as would be the case were the coolant to be introduced at a lower temperature to each cylinder individually, and not forced to flow around the entire engine.
- An engine according to the present invention solves the problems described above by providing a true modular construction for the power cylinders. In one embodiment, the cylinder carrier is itself modular. All of the present inventive engines utilize direct fresh water cooling, with individual cooling flows directed to each of the cylinder assemblies. In this manner, the present engine is ideally suited for charge air boosting to fairly high pressures, because the engine offers superior cooling capability as compared with prior art engines.
- A liquid-cooled internal combustion engine includes a plurality of cylinder assemblies mounted individually to a common cylinder carrier. Each cylinder assembly houses a single piston and has a cylinder portion with a cylinder bore, a cylinder head with at least one intake port, and at least one exhaust port, as well as at least one self-contained cooling passage. The present engine also includes a common-rail coolant inlet manifold for introducing an individual coolant flow to each of the self-contained cooling passages within the cylinder assemblies, and an exhaust manifold assembly mounted to each of the cylinder heads, with the exhaust manifold including a plurality of branch passages for receiving exhaust from each of the exhaust ports. The exhaust manifold further includes a number of separate intake coolant passages for conducting coolant flowing from each of the self-contained cooling passages in the cylinder head about an exterior portion of a mating one of each of the exhaust manifold's branch passages.
- The self-contained cooling passages in each cylinder assembly extend about the cylinder portion and cylinder head. The coolant is introduced by the coolant inlet manifold into each of the self-contained passages at a location proximate a lower portion of the cylinder portions, so that coolant is first permitted to flow about the cylinder portion, and then about the cylinder head, prior to being discharged into the exhaust manifold at a location proximate the exhaust port corresponding to the particular cylinder in question.
- Coolant for the cylinders and cylinder head of the present engine is circulated by means of a primary water pump which circulates either fresh water, or a glycol and water solution, through the cylinder assemblies and then through the cylinder heads into the exhaust manifold. While in the exhaust manifold, a heat exchanger mounted within the manifold transfers heat from coolant flowing from the cylinder assemblies to raw water flowing through a heat exchanger located in the exhaust manifold.
- In order to achieve excellent intercooling, a liquid-cooled charge air intercooler is furnished with raw water directly by a raw water pump. Similarly, a liquid-cooled engine oil cooler is furnished with raw water directly by the raw water pump. Raw water is also furnished directly to the previously described heat exchanger situated within the exhaust manifold.
- A secondary fluid cooler located downstream from the intercooler transfers heat from a secondary fluid, such as hydraulic fluid, or transmission fluid, or fuel, to raw water flowing from the intercooler.
- A turbocharger mounted on an engine according to the present invention preferably includes a cooling jacket for receiving raw water flowing from the oil cooler.
- According to another aspect of the present invention, a method for cooling a multi-cylinder internal combustion engine includes the steps of cooling a number of cylinder assemblies by providing an individual flow of fresh water to each of a corresponding number of discrete cooling passages. A separate, discrete cooling passage is routed to and through each of the cylinder assemblies. The present method also includes the step of extracting heat from the fresh water flowing from the cylinder assemblies by means of a direct raw water cooled heat exchanger. The present method also includes the step of extracting heat from a charge air intercooler by providing a direct raw water flow to the intercooler. Finally, the present method may include the step of extracting heat from lubricating oil flowing through the engine by means of a heat exchanger cooled by direct raw water flow.
- According to another aspect of the present invention, a cylinder carrier includes a plurality of cylinder mounting modules and a plurality of main bearing bulkheads interposed between and interconnecting adjacent ones of the cylinder mounting modules. A crankshaft is mounted to the main bearing bulkheads. The mechanical strength of the cylinder carrier is enhanced by structural rails, extending longitudinally along the periphery of the cylinder carrier, parallel to the crankshaft's centerline. These structural rails extend vertically and downwardly from a position above the centerline of the crankshaft, to an oil pan.
- Each of the cylinder mounting modules preferably comprises a light alloy casting, with each of the main bearing bulkheads preferably comprising a ferrous body. For example, cylinder mounting modules may be formed as aluminum castings, with the main bearing bulkheads being grey or nodular iron, cast steel or other ferrous compositions. As yet another alternative, not only the cylinder mounting modules, but also the main bearing bulkheads may be fabricated from a light alloy.
- The present engine further includes a single camshaft extending parallel to the crankshaft centerline. The camshaft operates at least one intake valve and at least one exhaust valve for each of the individual cylinder heads. The camshaft operates the valves by means of at least two rocker shafts extending across an upper portion of each of the cylinder heads in a direction generally perpendicular to the crankshaft centerline.
- According to another aspect of the present invention, a method for removing and reinstalling an individual cylinder assembly of an internal combustion engine includes the steps of draining coolant from the engine and removing a plurality of fasteners extending from a cylinder carrier upwardly through a cylinder portion and through a cylinder head. Thereafter, the cylinder head and cylinder portion are lifted from the engine and a wrist pin is shifted left or right within the piston so as to allow the piston to be separated from its connecting rod. Then, a new piston and wrist pin are installed upon the connecting rod and a new cylinder portion is installed upon the piston by sliding a piston ring compression zone of the cylinder portion over a plurality of piston rings carried upon the piston. Thereafter, the new cylinder portion is seated upon a pilot diameter formed in the cylinder carrier and the cylinder head is mounted upon the engine. Preferably, each of the cylinder portions has a ferrous cylinder sleeve pressed in place in the cylinder portion.
- According to another aspect of the present invention, a method for replacing crankshaft main bearing inserts in a reciprocating internal combustion engine includes the steps of removing an oil pan mounted to structural rails of the bottom of the engine's crankcase, and then removing at least one of the structural rails extending longitudinally along a portion of a cylinder carrier parallel to the crankshaft's centerline. The structural rail also extends vertically from a position above the centerline of the crankshaft to the oil pan. After the structural rail is removed, a number of main bearing caps will be removed serially from the cylinder carrier while replacing the main bearing inserts associated with each of the bearing caps. Thereafter, the engine is completed by reinstalling the previously removed structural rail and the oil pan.
- According to another aspect of the present invention, at least two valve lifters are provided for each cylinder. The lifters are slidingly housed within valve lifter sleeves mounted within bores formed in a deck surface of the engine's cylinder carrier. Each of the lifter sleeves includes a generally circular, hollow cylinder having a flange at one end, which engages a counterbore formed in the deck surface.
- According to another aspect of the present invention, each valve lifter has a center bore for feeding lubrication to a pushrod riding upon the lifter. A radially directed passage conducts lubricant to the center bore from an annular lubrication collection passage circumscribing a portion of the outer periphery of the valve lifter. Oil, which moves upwardly through the pushrods, is allowed to flow through drainback passages formed in the lifters, so that the camshaft's lobes are lubricated.
- According to yet another aspect of the present invention, a method for installing a cylinder poppet valve operating system in an internal combustion engine includes installing a camshaft in a cylinder carrier having a deck surface; installing a valve lifter sleeve in a bore formed through the deck surface; installing a valve lifter in the lifter sleeve; and installing a cylinder assembly upon the deck surface, such that the cylinder assembly contacts a portion of the valve lifter sleeve, whereby the valve lifter sleeve will be retained within the lifter bore. Then, a pushrod is installed through a passage within the cylinder assembly, such that the pushrod is in contact with an upper surface of the valve lifter. Finally, a rocker arm assembly may be installed upon a cylinder head mounted at an upper portion of the cylinder assembly.
- It is an advantage of an engine according to the present invention that a valve lifter and lifter sleeve arrangement allows the upper portion of the engine's cylinder assemblies to be lubricated without the need for the extensive machining which accompanies the provision of multiple oil passages in conventional engines.
- It is another advantage of an engine system according to the present invention that the engine's valve components may be replaced without resort to the expensive and time consuming machining services normally associated with the overhaul of valve lifter bores. This advantage results from the ability to remove and replace the lifter sleeves without the need of any machining devices.
- Other advantages, as well as features of the present invention, will become apparent to the reader of this specification.
-
FIG. 1 is a perspective view of an engine according to the present invention. -
FIG. 2 is similar toFIG. 1 , but shows the engine ofFIG. 1 with the exhaust manifold assembly removed. -
FIG. 3 illustrates various flow paths for the primary, or fresh water, cooling system of an engine according to the present invention. -
FIGS. 4A and 4B show an exhaust manifold according to the present invention. -
FIGS. 5A and 5B illustrates a liquid-cooled exhaust manifold suitable for use with a non-marine engine according to the present invention. -
FIG. 6 is a cutaway perspective view of a cylinder assembly according to the present invention. -
FIG. 7 is similar toFIG. 3 but shows additional aspects of a raw water cooling system and flows according to the present invention. -
FIG. 8 illustrates the flow path through an intercooler of an engine according to the present invention. -
FIG. 9 illustrates a primary or fresh water cooling system path of a non-marine engine according to the present invention and having a radiator. -
FIG. 10 is similar toFIG. 9 but shows the secondary cooling system path of a non-marine engine according to the present invention and having a radiator. -
FIG. 11 illustrates placement of the main bearing caps in an engine according to the present invention. -
FIG. 12 illustrates placement of a crankshaft within an engine according to the present invention. -
FIG. 13 illustrates a unitary cylinder carrier according to one aspect of the present invention having acylinder assembly 16 mounted thereto. -
FIG. 14 is an exploded view of a modular cylinder carrier according to one aspect of the present invention. -
FIG. 15 illustrates the components ofFIG. 14 after assembly into an engine carrier. -
FIG. 16 is a view, partially in section, and partially an elevation, showing a valve lifter sleeve, a valve lifter, and associated hardware according to the present invention. -
FIG. 17 is a perspective view of a valve lifter sleeve according to one aspect of the present invention. -
FIG. 18 is a perspective view of a valve lifter according to one aspect of the present invention. -
FIG. 19 is a plan view of a valve lifter ofFIG. 18 . -
FIG. 20 is a perspective view of a valve lifter slidingly carried within a valve lifter sleeve according to the present invention. -
FIG. 21 is an exploded perspective view of an engine showing various features according to the present invention. - As shown in
FIG. 1 ,engine 10 is an inline engine which is turbocharged and which has a liquid-cooled exhaust manifold for marine use. A primary water pump, 128, circulates fresh water throughexhaust manifold assembly 74, as well as through thecylinder assemblies 16, which are shown more clearly inFIGS. 2, 6 , and 13. As used herein, the term “fresh water” has the conventional meaning: i.e., coolant which is not extracted from a body of water upon which a vessel is being operated, but rather is cooled by a heat exchanger. Eachcylinder assembly 16, which is shown freestanding inFIG. 6 , includescylinder portion 18, having a cylinder bore 20, which is normally fitted with a honed iron sleeve.Cylinder portion 18 is preferably cast from a light alloy such as an aluminum or magnesium alloy. Alternatively, other metals such as iron could be employed for formingcylinder portion 18.Cylinder head 22 is mounted to an upper portion ofcylinder portion 18.Cylinder head 22, as shown inFIG. 6 , also includesintake port 26 andexhaust port 23. -
FIG. 13 depicts a fuel injector, 182, which may comprise either a diesel injector, a gasoline injector, a natural gas injector, a nitrous oxide injector, or yet other types of fuel injectors known to those skilled in the art and suggested by this disclosure. At least oneinjector 182 is mounted to each ofcylinder assemblies 16. -
FIGS. 1, 2 , 3, and 9 illustratecoolant supply manifold 68, which functions as a common rail to provide an individual coolant flow to self-contained cooling passages located within cylinder assembly 16 (FIG. 13 ). In essence, each ofcylinder assemblies 16 is provided with coolant, which has not flowed through other cylinder assemblies. As shown inFIG. 6 , coolant enterscylinder assembly 16 throughcoolant inlet port 46 and then travels throughwater jacket 48 located about cylinder bore 20. After circulating aboutwater jacket 48, coolant flows throughtransfer ports 52 and up into transverse cooling passage 56 formed withincylinder head 22. After having flowed through transverse cooling passage 56, coolant exitscylinder head 22 by means ofcoolant outlet ports 62. These coolant outlet ports are shown inFIG. 6 , as well as inFIG. 2 . - Fresh water coolant flowing from
outlet ports 62 of each ofcylinder heads 22 flows through ports 62A formed in exhaust manifold 74 (FIG. 4A ). Then, coolant flows aroundexhaust branch passages 80 and then throughinlet ports 98 and insideshell 96 of coolant heat exchanger 92 (FIG. 4B ). After enteringshell 96, coolant flows around the tubes oftube bundle 100 contained withincoolant heat exchanger 92. Then, coolant exitsheat exchanger 92 by flowing throughoutlet ports 102 formed inshell 96. Leavingheat exchanger 92, the fresh water coolant recirculates throughprimary water pump 128 and back throughcoolant inlet manifold 68 and intocylinder assemblies 16. -
Tube bundle 100 is cooled by means of a direct raw water flow provided byraw water pump 118 which is shown inFIGS. 1, 2 , 7, and 10. Raw water is furnished to one end oftube bundle 100 located at the front of the engine, as shown inFIG. 7 , and having traversed the length oftube bundle 100 and with the raw water traveling inside the numerous small tubes of the tube bundle, the raw water exits and flows intoexhaust elbow 58. Because raw water is provided directly tocoolant heat exchanger 92, high efficiency cooling is achieved, so as to allow high boosting rates with the present engine. - Turning now to
FIG. 7 ,raw water pump 118 hasinlet 120 which picks up raw water at ambient temperature from a lake, river, or ocean. The flow is immediately split into three separate flows. A first single flow passes throughengine oil cooler 124 and then to turbocharger coolingjacket 146, which surrounds a portion ofturbocharger 144. After flowing throughturbocharger cooling jacket 146, the water flows intoexhaust elbow 58. The second single flow of the raw water flow split fromraw water pump 118 flows, as previously described, through the engine's fresh water cooling system heat exchanger. - The third separate flow of the raw water split from the flow through
raw water pump 118 flows through intercooler coil 112 (not visible), located insideintake manifold 106 which is shown inFIG. 8 and receives direct raw water flow frompump 118. Air arriving atintake manifold 106 passes fromturbocharger 144 intoair inlet 110 and then flows upwardly throughintercooler heat exchanger 112 and intointake ports 26 ofcylinder assemblies 16 visible onFIG. 13 . Because raw water is provided directly to intercoolerheat exchanger coil 112, the raw water is at a much colder temperature than would otherwise be the case were the water to be used to cool some other part of the engine, such as the engine oil cooler, before enteringintercooler 112. This is not the case with known engines. - Raw
water leaving intercooler 112 passes throughsecondary fluid cooler 138, which is shown inFIG. 8 .Cooler 138 may be used for the purpose of extracting heat from transmission fluid, or other types of fluids used in a vehicle or boat having the present engine.Coolant expansion tank 132 is mounted at the opposite end of the engine fromsecondary fluid cooler 138.Expansion tank 132 accounts for the fact that known engine coolants generally have a positive coefficient of thermal expansion.Expansion tank 132 allows for this expansion without the necessity of admitting air into the cooling system. -
FIGS. 5A and 5B illustrate an exhaust manifold, 76, suitable for use with a non-marine variant of the present engine. Themanifold 76 ofFIGS. 5A and 5B is, however, liquid-cooled and the annulardischarge coolant passages 84 are readily ascertainable inFIG. 5A . - The manifold of
FIGS. 5A and 5B may be combined with the radiator, 126, illustrated inFIG. 9 . For the sake of clarity, the primary fresh water cooling system shown inFIG. 9 is separated from the secondary cooling system shown inFIG. 10 . In reality, both systems rely on the rejection of heat to the ambient air, whichradiators FIG. 10 , however, that a salient feature of the present invention resides in the fact that cooled water fromradiator 127, is used for the purpose of providing water to the cooling circuits furnished with raw water in the marine embodiments described earlier. Also in a vehicular system, the two cooling circuits would likely be combined into one, with the use of a single sufficiently large radiator and a single sufficiently large pump with a split pump discharge providing the coldest possible coolant flow to the engine coolant supply manifold, oil cooler, and intercooler. Cooling of the turbocharger is not normally required in a vehicular application. - Details of the bottom end of the present engine are shown in
FIGS. 11-15 . The engines shown inFIGS. 11, 12 and 13 include a unitary cylinder carrier, 30, providing a base for a plurality of cylinder assemblies 16 (FIG. 13 ).FIGS. 14 and 15 , on the other hand, show a modular cylinder carrier for a four-cylinder engine in which fourseparate mounting modules 156 are joined together by means of three main bearing bulkheads 160.Cylinder mounting modules 156 andbulkheads 160 are maintained in an assembly by means of threaded fasteners (not shown).FIG. 15 shows a completedcylinder carrier 30 which also includes an end bulkhead, 161, at the front of the engine.Bulkhead 161 has provisions for the front engine mounts. A rear bulkhead, 162, is provided for terminating the rear end of themodular cylinder carrier 30 shown inFIGS. 14 and 15 . It is easily seen fromFIGS. 14 and 15 that an engine according to the present invention may be assembled with varying numbers of cylinders merely by adding more or fewercylinder mounting modules 156 andbulkheads 160. - Regardless of the number of cylinders of
engine 10,FIGS. 11 and 12 illustrate a feature providing for ready disassembly and repair of the present engine even when the engine is mounted within a watercraft, a motor vehicle, or another piece of machinery.Cylinder carrier 30, whether of a one-piece configuration as shown inFIGS. 11, 12 and 13, or in a modular configuration as shown inFIGS. 14 and 15 , extends downwardly only to a position above the centerline of the crankshaft and main bearing bores. Thus, as shown inFIG. 12 , inserts 176 for each of the main bearings ofcrankshaft 166 may readily be removed fromengine 10 once the appropriate main bearing cap 168 (FIG. 11 ) has been removed. - Removal of main bearing inserts 176 is aided by the removability of structural rails 170 (
FIGS. 1 & 2 ).Structural rails 170 are used on both sides ofengine 10. In addition to providing rigidity equal to or better than would be available with a deep skirt cylinder block, rails 170 allow ready access to fasteners for main bearing caps 168 (FIG. 11 ). Afterrails 170 have been removed fromengine 10, as explained below, by removing the fasteners fromoil pan 174,crankshaft bearings 176 are exposed, as may be visualized fromFIGS. 11 and 12 . - According to another aspect of the present invention, a method for replacing crankshaft main bearing inserts in a reciprocating internal combustion engine includes the steps of removing
oil pan 174 and then removingstructural rail 170 from at least one side ofengine 10.Structural rail 170,oil pan 174, andcylinder carrier 30 are attached to another by means of through bolts 172 (FIG. 1 ) which extend throughoil pan 174, and then through passages formed instructural rails 170, and into suitably tapped holes withincarrier 30. Oncestructural rail 170 has been removed from the engine, main bearing caps 168 may be removed serially and the bearing inserts renewed using conventional techniques. - The present engine, whether having either a modular, or a
non-modular cylinder carrier 30, permits ready removal and reinstallation of an individual cylinder assembly. Experience shows that frequently, only one cylinder of an engine may be worn excessively. All too often with mono-block engines, it becomes necessary to scrap the entire block because it is not possible to rebore the cylinder. Even if reboring is an option, in an engine application such as a pleasure boat, it is not possible to machine anything on the cylinder block without removing the engine from the boat. Such removal is extremely costly, and particularly so, in the case of boats having multiple decks above the engine room. - In contrast with prior art engines, with the present inventive engine it is possible to replace a cylinder assembly, including the piston, and, if necessary, the connecting rod, without removing the engine from a boat or other vehicle. Should removal of a marine variant of the present engine become necessary, however, the engine may be removed without the necessity of cutting an access hole in either the decks or hull of a boat, because once
cylinder heads 22 andcylinder portions 18, as well aspistons 32, and connecting rods 40 (FIG. 6 ) have been removed from the engine, along withstructural rails 170, oil pan 174 (FIGS. 1 & 2 ), crankshaft 166 (FIGS. 12 & 13 ), and other small components,carrier 30 may be removed without the need for lifting equipment, which is generally unavailable below decks in most boats. - If it becomes necessary to remove and reinstall an
individual cylinder assembly 16 ofengine 10 according to the present invention, the steps for such removal and reinstallation include draining coolant fromengine 10, removing a plurality offasteners 172 extending fromcylinder carrier 30 upwardly throughcylinder portion 18 andcylinder heads 22, and liftingcylinder head 22 andcylinder portion 18 fromcarrier 30. Then,wrist pin 36 may be removed and a new piston, 32, installed upon connectingrod 40. Thereafter,cylinder portion 18 may be slidably installed uponpiston 32 by sliding piston ring compression zone 178 (FIG. 6 ) overpiston 20 and its piston rings. In essence, pistonring compression zone 178 makes it possible to reinsertpistons 32 into the bottom of cylinder bores 20 without the need of any additional ring compressor or other device. Also, it should be noted that with the exception ofcrankshaft 166, no machining is required to rebuild an engine according to the present invention. -
FIGS. 12 and 16 illustrate aspects of the valve actuation portion of the present engine system.Carrier 30 hascrankshaft 166 andcamshaft 186 installed therein, withcamshaft 186 having a plurality of lobes, 190, which actuate the valve train as follows.Valve lifters 200 are situated withinvalve lifter sleeves 194, which in turn are sited within valve lifter bores 192 formed withincylinder carrier 30. Note that bore 192 has a counter bore, 196, which, as noted below, engages a flange formed at an end portion ofvalve lifter sleeve 194. Continuing now withFIG. 16 ,valve lifter 200 is mounted withinvalve lifter sleeve 194 and contacts a lower end of a push rod, 204. Whencam lobe 190 raiseslifter 200,push rod 204 will correspondingly be raised. Pushrod 204 passes through thecylinder portion 18 ofcylinder assembly 16 through a passageway, 208, to an upper portion ofcylinder assembly 16. -
FIG. 17 shows various details ofvalve lifter sleeve 194.Sleeve 194 is configured as a generally circular hollow cylinder having a cylindricalouter surface 218 and anupper flange 222, which engages counter bore 196 formed indeck 200 ofcarrier 30.Flange 222 preventslifter sleeve 194 from moving downwardly within valve lifter bore 192 past the design location forlifter sleeve 194. In essence,lifter sleeve 194 is mounted in a depending orientation withinlifter bore 192. - As shown in
FIG. 17 ,valve lifter sleeve 194 has an annular groove, 226, in the upper surface ofupper flange 222, which provides a mounting location for a sealing O-ring (not shown) which is engaged bycylinder portion 18 ofcylinder assembly 16 whencylinder portion 18 is bolted tocarrier 30. Accordingly,cylinder assembly 16 preventslifter sleeve 194 from becoming disengaged withcarrier 30. - Lifter
sleeve 194 has an indexing surface or flatted area, 214, aligned with an elongated, radially directed oil passage, 228.Passage 228 receives oil from a pressurized oil galley, 197 (FIG. 16 ), withincarrier 30 and allows oil to pass through to lifter 200, as described below.Indexing feature 214 preventslifter sleeve 194 from rotating to a position at whichoil passage 228 is not properly indexed withoil passage 197. - As shown in
FIG. 18 ,lifter 200 has a generally cylindrical body, 230, with a lower end, 234, which is adapted for contact with one oflobes 190 ofcamshaft 186.Body 230 oflifter 200 also has an upper end, 240, having a hemispherical depression, 238, shown with specificity inFIG. 18 .Hemispherical depression 238 engages one of valve operatingpush rods 204 as shown inFIG. 16 . - Each of
valve lifters 200 has a center bore, 242, which feed oil up throughhollow push rods 204 to the upper part ofcylinder assembly 16. The oil is furnished to center bore 242 by means of a radially directed passage, 246, formed inlifter body 230. Radially directedpassage 246 allows communication with an annular lubrication collection passage, 250, which circumscribes a portion of the outer cylindrical surface oflifter body 230. In essence,passage 228 formed inlifter sleeve 194 is located so as to be in hydraulic communication with annularlubrication collection passage 250 formed inlifter body 230. As a result pressurized oil is fed through center bore 242 to pushrods 204, as described above. - Once engine oil has been used in the upper portion of
cylinder assembly 16 to lubricate valve guides and the rocker shafts and associated equipment, oil drains back throughpassages 208 and then drains down throughlifter body 230 through a number of drainback passages, 254, located radially outward from center bore 242.Drainback passages 254 extend axially through the greater part ofvalve lifter body 230 so that lubricating oil will be allowed to flow down throughbody 230 and then to exit into drainback annulus 258 (FIG. 19 ), from which the oil drains down over the lowermost portion of the outer surface oflifter body 230, and then onto camshaft 186 (FIG. 16 ). -
FIG. 21 is an exploded perspective view showingunitary carrier 30, with a structural rail, 170, andoil pan 174, according to the present invention.FIG. 21 also shows assembly ofvalve lifter sleeves 194 andvalve lifters 200 into lifter bores 192, complete with counter bores 196 withincylinder carrier 30.FIG. 21 shows thatvalve lifters 200 are telescopically nested intovalve lifter sleeves 194. As noted above, the use ofvalve lifter sleeves 194 permits an engine constructed according to the present invention to be rebuilt in the field without the use of expensive machining services and indeed, without the necessity of removing an engine from a vehicle or watercraft or other piece of equipment. Contrary to usual practice, it is not necessary to re-bore a cylinder block in the event that the valve lifter has failed and damaged the bore in which it is housed. Rather,sleeves 194 may be removed and replaced with new sleeves andnew lifters 200, allowing the engine to be placed back in service without machine shop work to the cylinder block. - While particular embodiments of the invention have been shown and described, numerous variations and alternate embodiments will occur to those skilled in the art. Accordingly, it is intended that the invention be limited only in terms of the appended claims.
Claims (13)
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PCT/US2008/058827 WO2008144112A1 (en) | 2007-05-21 | 2008-03-31 | Multicylinder internal combustion engine with individual cylinder assemblies |
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US11/751,138 US7543558B2 (en) | 2004-11-10 | 2007-05-21 | Multicylinder internal combustion engine with individual cylinder assemblies |
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US11/163,957 Continuation-In-Part US7419031B2 (en) | 2004-11-10 | 2005-11-04 | Integrally damped composite aircraft floor panels |
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